US20180340545A1 - Thrust Bearing System and Method For Operating The Same - Google Patents
Thrust Bearing System and Method For Operating The Same Download PDFInfo
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- US20180340545A1 US20180340545A1 US15/986,205 US201815986205A US2018340545A1 US 20180340545 A1 US20180340545 A1 US 20180340545A1 US 201815986205 A US201815986205 A US 201815986205A US 2018340545 A1 US2018340545 A1 US 2018340545A1
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- fluid
- turbine
- balance disk
- recited
- bearing
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- 238000001914 filtration Methods 0.000 claims 1
- 230000008569 process Effects 0.000 description 14
- 238000005461 lubrication Methods 0.000 description 11
- 230000001050 lubricating effect Effects 0.000 description 5
- 239000000356 contaminant Substances 0.000 description 4
- 238000013461 design Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
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- 238000012545 processing Methods 0.000 description 2
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- 230000008859 change Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 239000011796 hollow space material Substances 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
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- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/04—Units comprising pumps and their driving means the pump being fluid driven
- F04D13/043—Units comprising pumps and their driving means the pump being fluid driven the pump wheel carrying the fluid driving means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
- F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/04—Units comprising pumps and their driving means the pump being fluid driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
- F04D29/0416—Axial thrust balancing balancing pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
- F04D29/5866—Cooling at last part of the working fluid in a heat exchanger
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
Definitions
- the present disclosure relates generally to a fluid machine, and, more specifically, to thrust bearing lubrication for axial thrust force compensation within the fluid machine suitable for high contaminant or gas bubble environments.
- Rotating fluid machines are used in many applications for many processes. Lubrication for a rotating fluid machine is important. Various types of fluid machines use a thrust bearing that is lubricated by the pumpage. Adequate flow of pumpage should be supplied to obtain proper lubrication. Fluid machines are used under various conditions. During normal operating conditions, lubrication may be relatively easy. However, under various operating conditions contaminants or bubbles may be present in the pumpage. Contaminants and pumpage may affect the lubrication provided by the thrust bearing. Losing lubrication may cause damage the fluid machine. Air entrainment or debris within the pumpage may cause upset conditions.
- a hydraulic pressure booster (HPB) 10 is one type of fluid machine.
- the hydraulic pressure booster 10 is part of an overall processing system 12 that also includes a process chamber 14 .
- Hydraulic pressure boosters may include a pump portion 16 and a turbine portion 18 .
- a common shaft 20 extends between the pump portion 16 and the turbine portion 18 .
- the HPB 10 may be free-running which means that it is solely energized by the turbine and will run at any speed where the equilibrium exists between a turbine output torque and the pump input torque.
- the rotor or shaft 20 may also be connected to an electric motor to provide a predetermined rotational rate.
- the hydraulic pressure booster 10 is used to boost the process feed stream using energy from another process stream which is depressurized through the turbine portion 18 .
- the pump portion 16 includes a pump impeller 22 disposed within a pump impeller chamber 23 .
- the pump impeller 22 is coupled to the shaft 20 .
- the shaft 20 is supported by a bearing 24 .
- the bearing 24 is supported within a casing 26 . Both the pump portion 16 and the turbine portion 18 may share the same casing structure.
- the pump portion 16 includes a pump inlet 30 for receiving pumpage and a pump outlet 32 for discharging fluid to the process chamber 14 . Both of the pump inlet 30 and the pump outlet 32 are openings within the casing 26 .
- the turbine portion 18 may include a turbine impeller 40 disposed within a turbine impeller chamber 41 .
- the turbine impeller 40 is rotatably coupled to the shaft 20 .
- the pump impeller 22 , the shaft 20 and the turbine impeller 40 rotate together to form a rotor 43 .
- Fluid flow enters the turbine portion 18 through a turbine inlet 42 through the casing 26 .
- the turbine inlet 42 receives high-pressure fluid and the outlet 44 provides fluid at a pressure reduced by the turbine impeller 40 .
- the impeller 40 is enclosed by an impeller shroud.
- the impeller shroud includes an inboard impeller shroud 46 and an outboard impeller shroud 48 .
- the impeller shroud 48 is forced in the direction of a thrust bearing 54 .
- the thrust bearing 54 may be lubricated by pumpage fluid provided from the pump inlet 30 to the thrust bearing 54 through an external tube 56 .
- a gap or layer of lubricating fluid may be disposed between the thrust bearing 54 and outboard impeller shroud which is small and is thus represented by the space 55 therebetween.
- a filter 58 may be provided within the tube to prevent debris from entering the thrust bearing 54 .
- the pressure in the pump portion 16 is greater than the thrust bearing and thus lubricating flow will be provided to the thrust bearing 54 .
- the pressure within the turbine portion 18 will increase and thus fluid flow to the thrust bearing 54 may be reduced.
- the thrust bearing 54 may have inadequate lubricating flow during operation.
- the filter 58 becomes clogged, flow to the thrust bearing 54 may be interrupted.
- the thrust bearing 54 generates a force during normal operation in the opposite direction of arrow 50 .
- FIG. 2 a first example of a hydraulic-pressure booster 10 ′′ is illustrated.
- a hollow shaft 20 ′ is used rather than the solid shaft illustrated in FIG. 1 .
- the hollow shaft 20 ′ has a shaft passage 70 that is used for passing pumpage from the impeller chamber 23 of the pump portion 16 to the turbine portion 18 .
- the passage 20 may provide pumpage from the pump inlet 30 .
- the inboard shroud 46 ′ includes radial passages 72 .
- the radial passages 72 are fluidically coupled to the shaft passage 70 . Although only two radial passages 72 are illustrated, multiple radial passages may be provided.
- the impeller 40 ′ may include vanes 76 A-D as is illustrated in FIG. 3 .
- the impeller 40 ′ includes axial passages 74 .
- the axial passages 74 may be provided through vanes 76 A and 76 C of the impeller 40 ′.
- the axial passages are parallel to the axis of the HPB 10 ′′ and the shaft 20 ′.
- the axial passages 74 extend partially through the inner impeller shroud 46 ′ and entirely through the outboard impeller shroud 48 ′.
- the axial passages 74 terminate adjacent to the thrust bearing 54 . Again the gap between the outboard impeller shroud 48 ′ and the thrust bearing 54 is small and thus is represented by the line 55 in the Figure therebetween.
- the lubrication path for the thrust bearing 54 includes the shaft passage 70 , the radial passages 72 and the axial turbine impeller passages 74 .
- the highest pressure in the pumpage occurs in the pump inlet 30 during startup. Passages downstream of the pump inlet are at lower pressure and thus fluid from the pump portion 16 flows to the turbine portion 18 . Consequently, pumpage from the inlet is high during the startup. During shutdown of the equipment, the same factors apply due to the differential and pressure between the pump and the turbine. During normal operation, the highest pressure is no longer in the pump inlet but is at the pump outlet 32 . Due to the arrangement of the lubrication passages, the pressure increases in the pumpage due to a pressure rise occurring in the radial passage 72 due to a centrifugal force generated by the rotation of the turbine impeller 40 ′. The amount of pressure generation is determined by the radial length of the radial passages 72 and the rate of the rotor rotation. Consequently, pumpage is provided to the thrust bearing at the startup, normal operation and shutdown of the fluid machine 10 ′′.
- the impeller 40 ′ is illustrated having four impeller vanes 76 A- 76 D.
- the vanes extend axially relative to the axis of the shaft 20 ′.
- More than one impeller vane may have an axial passage 74 .
- the axial passage 74 extends through the vanes 76 and the inboard impeller shroud 46 ′ sufficient to intercept radial passage 72 and the outboard impeller shroud 48 ′ which are illustrated in FIG. 2 .
- the process chamber 14 is suitable for various types of processes including a reverse osmosis system.
- the process chamber may have a membrane 90 disposed therein.
- a permeate output 92 may be provided within the process chamber for desalinized fluid to flow therefrom.
- Brine fluid may enter the turbine inlet 42 .
- various types of process chambers may be provided for different types of processes including natural gas processing and the like.
- a deflector 110 is provided within the pump inlet 30 .
- the deflector 110 may be coupled to the pump impeller 22 using struts 112 .
- the struts 112 may hold the deflector 110 away from the pump impeller so that a gap is formed therebetween that allows fluid to flow into the shaft passage 70 .
- the deflector 110 may be cone-shaped and have an apex 114 disposed along the axis of the shaft 20 ′.
- the cone shape of the deflector 110 will deflect debris in the pumpage into the pump impeller 22 and thus prevent passage of debris into the shaft passage 70 .
- the debris is deflected away from the shaft passage 70 and thus will not clog the shaft passage 70 .
- the thrust bearing 54 ′ may include an outer land 210 and an inner land 212 .
- a fluid cavity 214 is disposed between the outer land 210 , the inner land 212 and the outer shroud 48 ′. It should be noted that the thrust bearing 54 ′ of FIG. 5 may be included in the examples illustrated in FIGS. 2 and 4 .
- the outer land 210 is disposed adjacent to the annular clearance 60 .
- the inner land 212 is disposed adjacent to the turbine outlet 44 .
- the thrust bearing 54 ′ may be annular in shape and thus the outer land 210 and inner land 212 may also be annular in shape.
- the cavity 214 may receive pressurized fluid from the pump portion 16 illustrated in FIGS. 2 and 4 . That is, pumpage may be received through the shaft passage 70 , the radial passages 72 and the axial passages 74 .
- Slight axial movements of the shaft 20 in the attached impeller shroud 48 ′ may cause variations in the axial clearance 220 between the lands 210 and 212 relative to the outer shroud 48 ′. If the axial clearances 220 increase, the pressure in the fluid cavity 214 decreases due to an increase of leakage through the clearances 220 . Conversely, if the axial gap of the clearance 220 decreases, the pressure will rise in the fluid cavity 214 . The pressure variation counteracts the variable axial thrust generated during operation and ensures that the lands 210 and 212 do not come into contact with the impeller shroud 48 ′.
- the reduction in pressure is determined by the flow resistance in the passages 70 - 74 .
- the passages are sized to provide a relationship between the rate of leakage and the change in pressure in the fluid cavity 214 as a function of the axial clearance.
- the radial location of the passage 74 determines the amount of centrifugally generated pressure rise and is considered in ensuring an optimal leakage in addition to the diameters of the flow channel. Excessive leakage flow may impair the efficiency and insufficient fluid flow will allow clearances to be too small and allow frictional contact during operation.
- the pressure in the fluid cavity is higher than the turbine outlet 44 and the pressure in the outer diameter of the impeller in the annular clearance 60 when the passage 74 is at the optimal radial location. Leakage will thus be out of cavity 214 to allow a desired pressure variation within the fluid cavity 214 .
- FIG. 6 an example similar to that of FIG. 5 is illustrated.
- the inner land 212 is replaced by a bushing 230 .
- the bushing 230 may form a cylindrical clearance relative to the impeller wear ring 232 .
- the fluid cavity 214 is thus defined between the wear ring 232 , the bushing 230 and the outer land 210 .
- vane 240 of an impeller 242 having curvature in the axial plane as well as the radial plane is illustrated.
- the impeller 242 may be used in a mixed flow design.
- the outer land 210 ′ and inner land 212 ′ are formed according to the shape of the impeller 242 .
- the fluid cavity 214 ′ may also be irregular in shape between the outer land 210 ′ and the inner land 212 ′.
- the fluid passage 250 provides fluid directly to the fluid cavity 214 ′ in a direction at an angle to the longitudinal axis of the fluid machine and shaft 20 ′.
- the radial passages 72 and axial passages 74 are replaced with the diagonal passage 250 .
- the diagonal passage 250 may enter the fluid cavity 214 ′ at various locations including near the land 212 ′ or at another location such as near land 210 ′. Various places between land 210 ′ and 212 ′ may also receive the diagonal passage 250 .
- the present disclosure provides an improved method for lubricating a rotating process machine during operation.
- the system provides pumpage to the thrust bearing over the entire operating range of the device.
- a fluid machine comprises a pump portion having a pump impeller chamber, a pump inlet and a pump outlet, a turbine portion having a turbine impeller chamber, a turbine inlet and a turbine outlet and a shaft extending between the pump impeller chamber and the turbine impeller chamber.
- the fluid machine also includes a first bearing and a second bearing spaced apart to form a balance disk chamber.
- a balance disk is coupled to the shaft and is disposed within the balance disk chamber and a turbine impeller coupled to the impeller end of the shaft disposed within the impeller chamber.
- a first thrust bearing is formed between the balance disk and the first bearing. The thrust bearing receives fluid from at least one of the pump inlet or the turbine outlet.
- a method for operating a fluid machine includes communicating fluid from a pump outlet or a turbine inlet to a thrust bearing formed by a balance disk coupled to a shaft, rotating the balance disk between a first bearing and a second bearing, and generating an axial force in response to communicating fluid in response to communicating and generating.
- FIG. 1 is a cross-sectional view of a first turbocharger according to the prior art.
- FIG. 2 is a cross-sectional view of a first fluid machine according to the prior art.
- FIG. 3 is an end view of an impeller of FIG. 2 .
- FIG. 4 is a cross-sectional view of a second fluid machine according to the prior art.
- FIG. 5 is a cross-sectional view of a third example of a turbine portion according to the prior art.
- FIG. 6 is a cross-sectional view of a fourth example of a turbine portion according to the prior art.
- FIG. 7 is a cross-sectional view of an alternative example of an impeller of the prior art.
- FIG. 8A is a cross-sectional view of a first example according to the present disclosure.
- FIG. 8B is a front view of the balance disk of FIG. 8A .
- FIG. 8C is a cross-sectional view of the balance disk relative to a bearing surface of FIG. 8A .
- FIG. 8D is a cross-sectional view of a second example according to the present disclosure.
- FIG. 8E is a cross-sectional view of a third example according to the present disclosure
- FIG. 9 is a fourth example of a hydraulic pressure booster according to a second example of the disclosure.
- a hydraulic pressure booster having a turbine portion and pump portion is illustrated.
- the present disclosure applies equally to other fluid machines.
- the present disclosure provides a way to deliver pumpage to a thrust bearing over the operating range of the device. Debris entering the turbine is also reduced.
- the hydraulic pressure booster 910 includes a first bearing 912 and a second bearing 914 that are spaced apart.
- the bearing 912 may be referred to as a turbine bearing and the bearing 914 may be referred to as a pump bearing.
- the pump bearing 914 and turbine bearing 912 define a balance disk chamber 916 .
- the balance disk chamber 916 houses a balance disk 918 which is rotatably coupled to the common shaft 20 .
- the bearing 912 has a first side 912 A that is disposed adjacent to the turbine impeller 40 and a second side 912 B within the balance disk chamber 916 .
- the bearing 914 has a first side 914 A adjacent to the pump impeller 22 and a second side 914 B within the balance disk chamber 916 .
- the bearings 912 and 914 provide radial support for the shaft 920 .
- the turbine outlet 44 is coaxial with the shaft 20 .
- the balance disk 918 has a first surface 918 A that faces surface 912 B and a second surface 918 B that faces the second surface 914 B.
- Surface 918 A has a land 930 .
- the second surface 918 B has a second land 932 .
- the lands 930 and 932 are annular in shape. In an alternate example, the land 930 may be disposed on the surface 912 B. Land 932 may also be disposed on the surface 914 B.
- a first thrust bearing 940 is defined by the volume between the first surface 912 B, surface 918 A and the first land 930 .
- a second thrust bearing 942 is defined between the surface 914 B, surface 918 B and the land 932 .
- the thrust bearings 940 , 942 are provided with process fluid from either the turbine flow or the feed flow as will be defined below. Fluid is communicated to the first thrust bearing 940 through an inlet port 944 . Fluid is communicated to the second thrust bearing 942 through a port 946 .
- the port 944 is in fluid communication with a channel 948 that extends through the bearing 912 and the casing 26 .
- a channel 950 is in fluid communication with the port 946 through the bearing 914 and the casing 26 .
- Another channel 952 may extend through the casing 26 and provide fluid adjacent to the balance disk 918 .
- a first pipe 954 may communicate fluid to the first channel 948 .
- a second pipe 956 communicates processed fluid to the channel 950 .
- Pipe 958 communicates fluid to the channel 950 .
- Each of the pipes 954 , 956 and 958 may be in communication with a four-way valve 960 .
- the four-way valve 960 selectively communicates fluid to the pipes 954 - 956 . It should be noted that the four-way valve 960 may receive fluid from a filter 962 .
- the filter 962 filters out contaminants from the process fluid before reaching the pipes 954 - 958 . Fluid from the filter 962 is communicated through a pipe 964 .
- the four-way valve 960 may be eliminated if the hydraulic pressure booster 910 is used in one or selected operating conditions. That is, the loads acting on the shaft from the turbine impeller 40 or the pump impeller 22 may always act in a constant direction during operation. Thus, one of the channels 948 - 952 may be provided in the design while eliminating the others.
- a three-way valve 970 is in communication with the turbine inlet 42 and the pump outlet 32 through pipes 972 and 974 , respectively.
- a counter thrust to balance the thrust of the rotor is provided with the balance disk 918 and the thrust bearings 940 and 942 associated therewith.
- lubrication flow may be admitted through the pipe 954 and into the channel 948 where it enters to form a thrust bearing through the port 944 .
- Fluid enters the pipe through the four-way valve 960 , the pipe 958 and the filter 962 . Fluid may be communicated into the filter 962 through the three-way valve 970 which operates to provide fluid from either the turbine inlet 42 or the pump outlet 32 .
- the three-way valve 970 may be controlled by a controller 980 which may be microprocessor-based.
- the controller 980 may also control the operation of the four-way valve 960 .
- lubrication flow may be admitted through channel 950 and pipe 956 . Fluid is communicated through the four-way valve 960 , the three-way valve 970 and from one of the turbine inlet 42 or the pump outlet 32 .
- the balance disk 918 may be provided with a plurality of radially oriented surface recesses that generate hydrodynamic lift that increases in strength as the gap between the balance disk and the adjacent bearing face decreases.
- a first plurality of recesses 982 A extends from the outer periphery of the balance disk 918 to just short of a groove 984 .
- the groove 984 is a reduced thickness portion.
- each surface 918 A, 918 B of the balance disk may include such surfaces. However, only one surface in various designs may be used.
- the recesses 982 B extend from the groove 984 to just short of the outer periphery of the balance disk 918 .
- the recesses 982 A and 982 B are interspersed. That is, when traversing around the balance disk 918 , the recesses 982 A alternate with recesses 982 B. In this example, there are four recesses 982 A and four recesses 982 B.
- FIG. 8C a cross-sectional view of the balance disk relative to one of the surfaces 912 B or 914 B is set forth.
- the balance disk is moving in the direction indicated by the arrow 986 .
- Each of the recesses 982 A or 982 B may be formed according to the following.
- the recesses 982 A or 982 B include a tapered portion 988 .
- the groove 990 is on the leading edge and thus pressure is built up in the tapered portion 988 due to the movement of the balance disk 918 in the direction indicated by the arrow 986 .
- the clearance between the surfaces 912 B or 914 B and the balance disk 918 may be small.
- the clearance is smaller than the distance between the wear rings 232 .
- the balance disk 918 includes a flow channel 992 therethrough.
- the flow channel 992 extends within the balance disk 918 and communicates fluid from a first side of the balance disk to a second side of the balance disk 918 .
- fluid is communicated from the pump side 918 B of the balance disk 918 to the turbine side 918 A of the balance disk 918 .
- the flow channel 992 has a first axial portion 992 A that extends from the pump side 918 B proximate to or adjacent to the shaft 20 .
- a radial portion 992 B extends in a radial direction from the first axial portion 992 A.
- the radial portion 992 B extends away from the shaft 20 in a radial direction direction.
- a second axial portion 992 C couples the radial 992 B to the second side of the balance disk 918 .
- fluid flows from the first side 918 B of the balance disk 918 which corresponds to the pump side through the first axial portion 992 A, through the radial portion 992 B where the centrifugal forces cause an increase in the pressure of the fluid.
- the centrifugal force is caused by the high rate of rotation of the shaft 20 and the rotor associated therewith.
- Fluid exits to the second side 918 A of the balance disk 918 through the second axial portion 992 C into the thrust bearing formed on the first side 918 A.
- the second axial portion 992 C is located a further distance from the shaft 20 than the first axial portion 992 A (radially outward).
- the flow channel 992 consequently increases the capacity of the thrust bearing at the turbine side of the balance disk 918 .
- a plurality of flow channels may be included in the balance disk. To provide balanced forces, the flow channels may be symmetrically disposed about the balance disk 918 . It should also be noted that in FIG. 8D , the thrust forces that act on the shaft are in the direction toward the turbine side.
- FIG. 8E another embodiment of a flow channel within a balance disk 918 is set forth in a similar manner as that of FIG. 8D .
- the predominant forces are in the direction of the pump portion 16 . Therefore, a flow channel 994 is communicating fluid from the first side 918 A of the balance disk which corresponds to the turbine portion to the second side 918 B of the balance disk which corresponds to the pump side of the balance disk 918 .
- the flow channel 994 includes a first axial portion 994 A that is fluidically coupled to the first side 918 A of the balance disk 918 .
- a radial portion 994 B communicates fluid from the first axial portion 994 A to a second axial portion 994 C.
- the second axial portion 994 C communicates fluid to the second side 918 B of the balance disk.
- fluid enters the first axial portion 994 A adjacent to or proximate to the shaft 20 .
- the pressure of the fluid within the flow channel 994 is increased by the centrifugal forces acting on the rotating balance disk 918 .
- the fluid pressure increases within the radial portion 994 B as the fluid traverses in the direction illustrated by the arrow toward the outward direction of the balance disk 918 away from the shaft 20 .
- Higher pressure fluid then enters the thrust bearing located at the pump side of the balance disk 918 .
- the increased high pressure fluid into the thrust bearing increases the capacity of the thrust bearing, in this case, on the pump side of the hydraulic pressure booster 910 .
- an alternative fluid machine 1010 is set forth.
- fluid is communicated from the pump outlet 32 to the filter 1011 disposed within a pipe 1012 .
- a pipe 1014 may communicate fluid from the pump outlet to the shaft 20 between the turbine portion 18 and the pump portion 16 of the fluid machine 1010 such as a hydraulic pressure booster.
- the balance disk 1030 and balance disk chamber 1042 have been relocated outboard and adjacent to the turbine portion 18 of the fluid machine.
- the casing 26 may be supplemented with a casing extension or outer cap 1020 that is fastened with a bolt 1022 to a turbine end of the casing 26 .
- the casing 26 and the outer cap 1020 may have a hollow space therebetween to house a first bearing 1024 and a second bearing 1026 .
- the bearings 1024 and the bearings 1026 have inner surfaces 1024 A and 1026 A, respectively.
- the surface 1024 A may form thrust bearing 1040 between surfaces 1030 A of the balance disk 1030 within the volume defined by the wear ring 1080 disposed on the surface 1030 A.
- the flow channels 992 , 994 illustrated in the balance disks illustrated in FIGS. 8D and 8E may also be incorporated within the balance disk 1030 to increase the capacity of the thrust bearings 1040 .
- a shaft extension 1032 may extend from the turbine portion 18 and the shaft 20 so that the balance disk 1030 and the wear ring 1080 rotates therewith.
- a shaft seal 1034 seals the shaft extension 1032 from leakage with the turbine outlet 44 .
- the turbine outlet 44 is perpendicular to the shaft 20 .
- the pipe 1014 and the channel 1014 A are provided closer to the pump impeller 22 than the turbine impeller 40 . That is, the distance between the pump impeller 22 and the channel 1014 A is less than the distance between the channel 1014 A and the turbine impeller 40 .
- the rate of flow to the thrust bearing 1040 formed by a volume within the balance disk chamber 1042 between the bearing casing 1020 , the balance disk 1030 and wear ring 1080 .
- a temperature sensor 1044 and a proximity sensor 1046 may be disposed within the bearing 1024 to generate a temperature signal corresponding to a temperature at the bearing 1024 and a proximity signal of the balance disk 1030 relative distance to the bearing 1024 .
- the output of the temperature sensor 1044 may be used to control the heat exchanger 1050 and thus cool the fluid within the thrust bearing 1040 .
- the fluid from the thrust bearing 1040 may be communicated through the heat exchanger 1050 and to the inlet pipe 1052 in a cooled state.
- the circulation through the heat exchanger 1050 is driven by the higher pressure caused by the rotating balance disk 1030 . That is, a higher pressure exists at the outer diameter of the balance disk 1030 and thus the fluid may be communicated through the heat exchanger and back through the inlet pipe 1052 .
- the speed sensor 1060 may be used to monitor the rotational speed of the shaft extension 1032 which also corresponds to the rotational speed of the shaft 20 .
- the speed sensor 1060 may be located within the turbine outlet 44 or adjacent to the temperature sensor 1044 and the proximity sensor 1046 .
- a tooth or other indicator on the balance disk may provide the sensor with the rotational speed of the shaft.
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- Engineering & Computer Science (AREA)
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
- Sliding-Contact Bearings (AREA)
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Abstract
Description
- This application claims the benefit of U.S. Provisional Application No. 62/509,914 filed on May 23, 2017. The disclosure of the above application is incorporated herein by reference.
- The present disclosure relates generally to a fluid machine, and, more specifically, to thrust bearing lubrication for axial thrust force compensation within the fluid machine suitable for high contaminant or gas bubble environments.
- The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.
- Rotating fluid machines are used in many applications for many processes. Lubrication for a rotating fluid machine is important. Various types of fluid machines use a thrust bearing that is lubricated by the pumpage. Adequate flow of pumpage should be supplied to obtain proper lubrication. Fluid machines are used under various conditions. During normal operating conditions, lubrication may be relatively easy. However, under various operating conditions contaminants or bubbles may be present in the pumpage. Contaminants and pumpage may affect the lubrication provided by the thrust bearing. Losing lubrication may cause damage the fluid machine. Air entrainment or debris within the pumpage may cause upset conditions.
- Referring now to
FIG. 1 , a hydraulic pressure booster (HPB) 10 is one type of fluid machine. Thehydraulic pressure booster 10 is part of anoverall processing system 12 that also includes aprocess chamber 14. Hydraulic pressure boosters may include apump portion 16 and aturbine portion 18. Acommon shaft 20 extends between thepump portion 16 and theturbine portion 18. The HPB 10 may be free-running which means that it is solely energized by the turbine and will run at any speed where the equilibrium exists between a turbine output torque and the pump input torque. The rotor orshaft 20 may also be connected to an electric motor to provide a predetermined rotational rate. - The
hydraulic pressure booster 10 is used to boost the process feed stream using energy from another process stream which is depressurized through theturbine portion 18. - The
pump portion 16 includes apump impeller 22 disposed within apump impeller chamber 23. Thepump impeller 22 is coupled to theshaft 20. Theshaft 20 is supported by abearing 24. Thebearing 24 is supported within acasing 26. Both thepump portion 16 and theturbine portion 18 may share the same casing structure. - The
pump portion 16 includes apump inlet 30 for receiving pumpage and apump outlet 32 for discharging fluid to theprocess chamber 14. Both of thepump inlet 30 and thepump outlet 32 are openings within thecasing 26. - The
turbine portion 18 may include aturbine impeller 40 disposed within aturbine impeller chamber 41. Theturbine impeller 40 is rotatably coupled to theshaft 20. The pump impeller 22, theshaft 20 and theturbine impeller 40 rotate together to form arotor 43. Fluid flow enters theturbine portion 18 through aturbine inlet 42 through thecasing 26. Fluid flows out of theturbine portion 40 through aturbine outlet 44 also through thecasing 26. Theturbine inlet 42 receives high-pressure fluid and theoutlet 44 provides fluid at a pressure reduced by theturbine impeller 40. - The
impeller 40 is enclosed by an impeller shroud. The impeller shroud includes aninboard impeller shroud 46 and anoutboard impeller shroud 48. During operation thepump impeller 22, theshaft 20 and theturbine impeller 40 are forced in the direction of theturbine portion 18. InFIG. 1 , this is in the direction of theaxial arrow 50. Theimpeller shroud 48 is forced in the direction of a thrust bearing 54. - The thrust bearing 54 may be lubricated by pumpage fluid provided from the
pump inlet 30 to the thrust bearing 54 through anexternal tube 56. A gap or layer of lubricating fluid may be disposed between the thrust bearing 54 and outboard impeller shroud which is small and is thus represented by thespace 55 therebetween. Afilter 58 may be provided within the tube to prevent debris from entering the thrust bearing 54. At start-up, the pressure in thepump portion 16 is greater than the thrust bearing and thus lubricating flow will be provided to the thrust bearing 54. During operation, the pressure within theturbine portion 18 will increase and thus fluid flow to the thrust bearing 54 may be reduced. The thrust bearing 54 may have inadequate lubricating flow during operation. Also, when thefilter 58 becomes clogged, flow to the thrust bearing 54 may be interrupted. The thrust bearing 54 generates a force during normal operation in the opposite direction ofarrow 50. - Referring now to
FIG. 2 , a first example of a hydraulic-pressure booster 10″ is illustrated. In this example, the common components fromFIG. 1 are provided with the same reference numerals are not described further. In this example, ahollow shaft 20′ is used rather than the solid shaft illustrated inFIG. 1 . Thehollow shaft 20′ has ashaft passage 70 that is used for passing pumpage from theimpeller chamber 23 of thepump portion 16 to theturbine portion 18. Thepassage 20 may provide pumpage from thepump inlet 30. - The
inboard shroud 46′ includesradial passages 72. Theradial passages 72 are fluidically coupled to theshaft passage 70. Although only tworadial passages 72 are illustrated, multiple radial passages may be provided. - The
impeller 40′ may includevanes 76A-D as is illustrated inFIG. 3 . Theimpeller 40′ includesaxial passages 74. Theaxial passages 74 may be provided throughvanes impeller 40′. The axial passages are parallel to the axis of theHPB 10″ and theshaft 20′. Theaxial passages 74 extend partially through theinner impeller shroud 46′ and entirely through theoutboard impeller shroud 48′. Theaxial passages 74 terminate adjacent to the thrust bearing 54. Again the gap between theoutboard impeller shroud 48′ and the thrust bearing 54 is small and thus is represented by theline 55 in the Figure therebetween. The lubrication path for thethrust bearing 54 includes theshaft passage 70, theradial passages 72 and the axialturbine impeller passages 74. - In operation, at start-up pressure within the
pump portion 16 is higher than theturbine portion 18. Fluid within the pump portion travels through theshaft passage 70 to theradial passages 72 and to theaxial passage 74. When the fluid leaves theaxial passage 74, the fluid is provided to thethrust bearing 54. More specifically, the fluid lubricates the space orgap 55 between thethrust bearing 54 and theoutboard impeller shroud 48′. Thethrust bearing 54 generates an inboard axial force in response to the lubricating fluid in the opposite direction ofarrow 50. - The highest pressure in the pumpage occurs in the
pump inlet 30 during startup. Passages downstream of the pump inlet are at lower pressure and thus fluid from thepump portion 16 flows to theturbine portion 18. Consequently, pumpage from the inlet is high during the startup. During shutdown of the equipment, the same factors apply due to the differential and pressure between the pump and the turbine. During normal operation, the highest pressure is no longer in the pump inlet but is at thepump outlet 32. Due to the arrangement of the lubrication passages, the pressure increases in the pumpage due to a pressure rise occurring in theradial passage 72 due to a centrifugal force generated by the rotation of theturbine impeller 40′. The amount of pressure generation is determined by the radial length of theradial passages 72 and the rate of the rotor rotation. Consequently, pumpage is provided to the thrust bearing at the startup, normal operation and shutdown of thefluid machine 10″. - Referring now to
FIG. 3 , theimpeller 40′ is illustrated having fourimpeller vanes 76A-76D. Various numbers of vanes may be provided. The vanes extend axially relative to the axis of theshaft 20′. More than one impeller vane may have anaxial passage 74. Theaxial passage 74 extends through the vanes 76 and theinboard impeller shroud 46′ sufficient to interceptradial passage 72 and theoutboard impeller shroud 48′ which are illustrated inFIG. 2 . - It should be noted that the
process chamber 14 is suitable for various types of processes including a reverse osmosis system. For a reverse osmosis system, the process chamber may have amembrane 90 disposed therein. Apermeate output 92 may be provided within the process chamber for desalinized fluid to flow therefrom. Brine fluid may enter theturbine inlet 42. Of course, as mentioned above, various types of process chambers may be provided for different types of processes including natural gas processing and the like. - Referring now to
FIG. 4 , an example similar to that ofFIG. 2 is illustrated and is thus provided the same reference numerals. In this example, adeflector 110 is provided within thepump inlet 30. Thedeflector 110 may be coupled to thepump impeller 22 usingstruts 112. Thestruts 112 may hold thedeflector 110 away from the pump impeller so that a gap is formed therebetween that allows fluid to flow into theshaft passage 70. - The
deflector 110 may be cone-shaped and have an apex 114 disposed along the axis of theshaft 20′. The cone shape of thedeflector 110 will deflect debris in the pumpage into thepump impeller 22 and thus prevent passage of debris into theshaft passage 70. Unlike thefilter 58 illustrated inFIG. 1 , the debris is deflected away from theshaft passage 70 and thus will not clog theshaft passage 70. - Referring now to
FIG. 5 , theturbine portion 18 is illustrated having another example of athrust bearing 54′. Thethrust bearing 54′ may include anouter land 210 and aninner land 212. Afluid cavity 214 is disposed between theouter land 210, theinner land 212 and theouter shroud 48′. It should be noted that the thrust bearing 54′ ofFIG. 5 may be included in the examples illustrated inFIGS. 2 and 4 . - The
outer land 210 is disposed adjacent to theannular clearance 60. Theinner land 212 is disposed adjacent to theturbine outlet 44. Thethrust bearing 54′ may be annular in shape and thus theouter land 210 andinner land 212 may also be annular in shape. - The
cavity 214 may receive pressurized fluid from thepump portion 16 illustrated inFIGS. 2 and 4 . That is, pumpage may be received through theshaft passage 70, theradial passages 72 and theaxial passages 74. - Slight axial movements of the
shaft 20 in the attachedimpeller shroud 48′ may cause variations in theaxial clearance 220 between thelands outer shroud 48′. If theaxial clearances 220 increase, the pressure in thefluid cavity 214 decreases due to an increase of leakage through theclearances 220. Conversely, if the axial gap of theclearance 220 decreases, the pressure will rise in thefluid cavity 214. The pressure variation counteracts the variable axial thrust generated during operation and ensures that thelands impeller shroud 48′. - The reduction in pressure is determined by the flow resistance in the passages 70-74. The passages are sized to provide a relationship between the rate of leakage and the change in pressure in the
fluid cavity 214 as a function of the axial clearance. The radial location of thepassage 74 determines the amount of centrifugally generated pressure rise and is considered in ensuring an optimal leakage in addition to the diameters of the flow channel. Excessive leakage flow may impair the efficiency and insufficient fluid flow will allow clearances to be too small and allow frictional contact during operation. - The pressure in the fluid cavity is higher than the
turbine outlet 44 and the pressure in the outer diameter of the impeller in theannular clearance 60 when thepassage 74 is at the optimal radial location. Leakage will thus be out ofcavity 214 to allow a desired pressure variation within thefluid cavity 214. - Referring now to
FIG. 6 , an example similar to that ofFIG. 5 is illustrated. Theinner land 212 is replaced by abushing 230. Thebushing 230 may form a cylindrical clearance relative to theimpeller wear ring 232. Thefluid cavity 214 is thus defined between thewear ring 232, thebushing 230 and theouter land 210. - Referring now to
FIG. 7 ,vane 240 of animpeller 242 having curvature in the axial plane as well as the radial plane is illustrated. Theimpeller 242 may be used in a mixed flow design. In this example, theouter land 210′ andinner land 212′ are formed according to the shape of theimpeller 242. Thefluid cavity 214′ may also be irregular in shape between theouter land 210′ and theinner land 212′. - The
fluid passage 250 provides fluid directly to thefluid cavity 214′ in a direction at an angle to the longitudinal axis of the fluid machine andshaft 20′. Thus, theradial passages 72 andaxial passages 74 are replaced with thediagonal passage 250. Thediagonal passage 250 may enter thefluid cavity 214′ at various locations including near theland 212′ or at another location such asnear land 210′. Various places betweenland 210′ and 212′ may also receive thediagonal passage 250. - Further areas of applicability will become apparent from the description provided herein. It should be understood that the description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure.
- This section provides a general summary of the disclosure, and is not a comprehensive disclosure of its full scope or all of its features.
- The present disclosure provides an improved method for lubricating a rotating process machine during operation. The system provides pumpage to the thrust bearing over the entire operating range of the device.
- In one aspect of the invention, a fluid machine comprises a pump portion having a pump impeller chamber, a pump inlet and a pump outlet, a turbine portion having a turbine impeller chamber, a turbine inlet and a turbine outlet and a shaft extending between the pump impeller chamber and the turbine impeller chamber. The fluid machine also includes a first bearing and a second bearing spaced apart to form a balance disk chamber. A balance disk is coupled to the shaft and is disposed within the balance disk chamber and a turbine impeller coupled to the impeller end of the shaft disposed within the impeller chamber. A first thrust bearing is formed between the balance disk and the first bearing. The thrust bearing receives fluid from at least one of the pump inlet or the turbine outlet.
- In another aspect of the invention, a method for operating a fluid machine includes communicating fluid from a pump outlet or a turbine inlet to a thrust bearing formed by a balance disk coupled to a shaft, rotating the balance disk between a first bearing and a second bearing, and generating an axial force in response to communicating fluid in response to communicating and generating.
- Further areas of applicability will become apparent from the description provided herein. The description and specific examples in this summary are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure.
- The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.
-
FIG. 1 is a cross-sectional view of a first turbocharger according to the prior art. -
FIG. 2 is a cross-sectional view of a first fluid machine according to the prior art. -
FIG. 3 is an end view of an impeller ofFIG. 2 . -
FIG. 4 is a cross-sectional view of a second fluid machine according to the prior art. -
FIG. 5 is a cross-sectional view of a third example of a turbine portion according to the prior art. -
FIG. 6 is a cross-sectional view of a fourth example of a turbine portion according to the prior art. -
FIG. 7 is a cross-sectional view of an alternative example of an impeller of the prior art. -
FIG. 8A is a cross-sectional view of a first example according to the present disclosure. -
FIG. 8B is a front view of the balance disk ofFIG. 8A . -
FIG. 8C is a cross-sectional view of the balance disk relative to a bearing surface ofFIG. 8A . -
FIG. 8D is a cross-sectional view of a second example according to the present disclosure. -
FIG. 8E is a cross-sectional view of a third example according to the present disclosure -
FIG. 9 is a fourth example of a hydraulic pressure booster according to a second example of the disclosure. - The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. For purposes of clarity, the same reference numbers will be used in the drawings to identify similar elements. As used herein, the phrase at least one of A, B, and C should be construed to mean a logical (A or B or C), using a non-exclusive logical OR. It should be understood that steps within a method may be executed in different order without altering the principles of the present disclosure.
- In the following description, a hydraulic pressure booster having a turbine portion and pump portion is illustrated. However, the present disclosure applies equally to other fluid machines. The present disclosure provides a way to deliver pumpage to a thrust bearing over the operating range of the device. Debris entering the turbine is also reduced.
- Referring now to
FIG. 8A , ahydraulic pressure booster 910 according to the present disclosure is set forth. In this example, the components with the same reference numerals described above inFIGS. 1-7 are set forth. In this example, thehydraulic pressure booster 910 includes afirst bearing 912 and asecond bearing 914 that are spaced apart. In this example, thebearing 912 may be referred to as a turbine bearing and thebearing 914 may be referred to as a pump bearing. Thepump bearing 914 andturbine bearing 912 define abalance disk chamber 916. Thebalance disk chamber 916 houses abalance disk 918 which is rotatably coupled to thecommon shaft 20. Thebearing 912 has afirst side 912A that is disposed adjacent to theturbine impeller 40 and asecond side 912B within thebalance disk chamber 916. Thebearing 914 has afirst side 914A adjacent to thepump impeller 22 and asecond side 914B within thebalance disk chamber 916. Thebearings turbine outlet 44 is coaxial with theshaft 20. - The
balance disk 918 has afirst surface 918A that facessurface 912B and asecond surface 918B that faces thesecond surface 914B.Surface 918A has aland 930. Thesecond surface 918B has asecond land 932. Thelands land 930 may be disposed on thesurface 912B.Land 932 may also be disposed on thesurface 914B. - A first thrust bearing 940 is defined by the volume between the
first surface 912B,surface 918A and thefirst land 930. A second thrust bearing 942 is defined between thesurface 914B,surface 918B and theland 932. The thrust bearing and theland 932. Thethrust bearings inlet port 944. Fluid is communicated to the second thrust bearing 942 through aport 946. Theport 944 is in fluid communication with achannel 948 that extends through thebearing 912 and thecasing 26. Achannel 950 is in fluid communication with theport 946 through thebearing 914 and thecasing 26. Anotherchannel 952 may extend through thecasing 26 and provide fluid adjacent to thebalance disk 918. - A
first pipe 954 may communicate fluid to thefirst channel 948. Asecond pipe 956 communicates processed fluid to thechannel 950.Pipe 958 communicates fluid to thechannel 950. - Each of the
pipes way valve 960. The four-way valve 960 selectively communicates fluid to the pipes 954-956. It should be noted that the four-way valve 960 may receive fluid from afilter 962. Thefilter 962 filters out contaminants from the process fluid before reaching the pipes 954-958. Fluid from thefilter 962 is communicated through apipe 964. - In operation, the four-
way valve 960 may be eliminated if thehydraulic pressure booster 910 is used in one or selected operating conditions. That is, the loads acting on the shaft from theturbine impeller 40 or thepump impeller 22 may always act in a constant direction during operation. Thus, one of the channels 948-952 may be provided in the design while eliminating the others. - A three-
way valve 970 is in communication with theturbine inlet 42 and thepump outlet 32 throughpipes - In operation, a counter thrust to balance the thrust of the rotor is provided with the
balance disk 918 and thethrust bearings arrow 50, which is toward the turbine portion, is present, lubrication flow may be admitted through thepipe 954 and into thechannel 948 where it enters to form a thrust bearing through theport 944. Fluid enters the pipe through the four-way valve 960, thepipe 958 and thefilter 962. Fluid may be communicated into thefilter 962 through the three-way valve 970 which operates to provide fluid from either theturbine inlet 42 or thepump outlet 32. The three-way valve 970 may be controlled by acontroller 980 which may be microprocessor-based. Thecontroller 980 may also control the operation of the four-way valve 960. - If the thrust is directed toward the pump side of the
HPB 910, lubrication flow may be admitted throughchannel 950 andpipe 956. Fluid is communicated through the four-way valve 960, the three-way valve 970 and from one of theturbine inlet 42 or thepump outlet 32. - As briefly mentioned above, it may also be desirable to communicate fluid simultaneously through the
pipes pipes pipe 958 communicates fluid to thechannel 952. Thechannel 952 provides fluid adjacent to the peripheral edge of thebalance disk 918. - Referring now to
FIG. 8B , to increase the thrust force, hydrodynamic action of thebalance disk 918 may be used. Thebalance disk 918 may be provided with a plurality of radially oriented surface recesses that generate hydrodynamic lift that increases in strength as the gap between the balance disk and the adjacent bearing face decreases. In this example, a first plurality ofrecesses 982A extends from the outer periphery of thebalance disk 918 to just short of agroove 984. Thegroove 984 is a reduced thickness portion. It should be noted that eachsurface recesses 982B extend from thegroove 984 to just short of the outer periphery of thebalance disk 918. Therecesses balance disk 918, therecesses 982A alternate withrecesses 982B. In this example, there are fourrecesses 982A and fourrecesses 982B. - Referring now to
FIG. 8C , a cross-sectional view of the balance disk relative to one of thesurfaces recesses recesses portion 988. Thegroove 990 is on the leading edge and thus pressure is built up in the taperedportion 988 due to the movement of thebalance disk 918 in the direction indicated by the arrow 986. - Because the lubrication flow to the thrust bearings are filtered, the clearance between the
surfaces balance disk 918 may be small. The clearance is smaller than the distance between the wear rings 232. - Referring now to
FIG. 8D , thebalance disk 918 includes aflow channel 992 therethrough. Theflow channel 992 extends within thebalance disk 918 and communicates fluid from a first side of the balance disk to a second side of thebalance disk 918. InFIG. 8D , fluid is communicated from thepump side 918B of thebalance disk 918 to theturbine side 918A of thebalance disk 918. - The
flow channel 992 has a firstaxial portion 992A that extends from thepump side 918B proximate to or adjacent to theshaft 20. Aradial portion 992B extends in a radial direction from the firstaxial portion 992A. Theradial portion 992B extends away from theshaft 20 in a radial direction direction. A secondaxial portion 992C couples the radial 992B to the second side of thebalance disk 918. - In operation, fluid flows from the
first side 918B of thebalance disk 918 which corresponds to the pump side through the firstaxial portion 992A, through theradial portion 992B where the centrifugal forces cause an increase in the pressure of the fluid. The centrifugal force is caused by the high rate of rotation of theshaft 20 and the rotor associated therewith. Fluid exits to thesecond side 918A of thebalance disk 918 through the secondaxial portion 992C into the thrust bearing formed on thefirst side 918A. The secondaxial portion 992C is located a further distance from theshaft 20 than the firstaxial portion 992A (radially outward). Theflow channel 992 consequently increases the capacity of the thrust bearing at the turbine side of thebalance disk 918. - It should be noted that a plurality of flow channels may be included in the balance disk. To provide balanced forces, the flow channels may be symmetrically disposed about the
balance disk 918. It should also be noted that inFIG. 8D , the thrust forces that act on the shaft are in the direction toward the turbine side. - Referring now to
FIG. 8E , another embodiment of a flow channel within abalance disk 918 is set forth in a similar manner as that ofFIG. 8D . However, inFIG. 8E , the predominant forces are in the direction of thepump portion 16. Therefore, aflow channel 994 is communicating fluid from thefirst side 918A of the balance disk which corresponds to the turbine portion to thesecond side 918B of the balance disk which corresponds to the pump side of thebalance disk 918. In this example, theflow channel 994 includes a firstaxial portion 994A that is fluidically coupled to thefirst side 918A of thebalance disk 918. Aradial portion 994B communicates fluid from the firstaxial portion 994A to a secondaxial portion 994C. The secondaxial portion 994C communicates fluid to thesecond side 918B of the balance disk. In a similar manner to that described above with respect toFIG. 8D , fluid enters the firstaxial portion 994A adjacent to or proximate to theshaft 20. The pressure of the fluid within theflow channel 994 is increased by the centrifugal forces acting on therotating balance disk 918. The fluid pressure increases within theradial portion 994B as the fluid traverses in the direction illustrated by the arrow toward the outward direction of thebalance disk 918 away from theshaft 20. Higher pressure fluid then enters the thrust bearing located at the pump side of thebalance disk 918. As mentioned above, the increased high pressure fluid into the thrust bearing increases the capacity of the thrust bearing, in this case, on the pump side of thehydraulic pressure booster 910. - Referring now to
FIG. 9 , analternative fluid machine 1010 is set forth. In this example, fluid is communicated from thepump outlet 32 to thefilter 1011 disposed within apipe 1012. Apipe 1014 may communicate fluid from the pump outlet to theshaft 20 between theturbine portion 18 and thepump portion 16 of thefluid machine 1010 such as a hydraulic pressure booster. In this example, thebalance disk 1030 andbalance disk chamber 1042 have been relocated outboard and adjacent to theturbine portion 18 of the fluid machine. Thecasing 26 may be supplemented with a casing extension orouter cap 1020 that is fastened with abolt 1022 to a turbine end of thecasing 26. Thecasing 26 and theouter cap 1020 may have a hollow space therebetween to house afirst bearing 1024 and asecond bearing 1026. Thebearings 1024 and thebearings 1026 haveinner surfaces surface 1024A may form thrustbearing 1040 betweensurfaces 1030A of thebalance disk 1030 within the volume defined by thewear ring 1080 disposed on thesurface 1030A. - The
flow channels FIGS. 8D and 8E may also be incorporated within thebalance disk 1030 to increase the capacity of thethrust bearings 1040. - A
shaft extension 1032 may extend from theturbine portion 18 and theshaft 20 so that thebalance disk 1030 and thewear ring 1080 rotates therewith. Ashaft seal 1034 seals theshaft extension 1032 from leakage with theturbine outlet 44. Theturbine outlet 44 is perpendicular to theshaft 20. - The
pipe 1014 and thechannel 1014A are provided closer to thepump impeller 22 than theturbine impeller 40. That is, the distance between thepump impeller 22 and thechannel 1014A is less than the distance between thechannel 1014A and theturbine impeller 40. - In operation, the rate of flow to the
thrust bearing 1040 formed by a volume within thebalance disk chamber 1042 between the bearingcasing 1020, thebalance disk 1030 and wearring 1080. - A
temperature sensor 1044 and aproximity sensor 1046 may be disposed within thebearing 1024 to generate a temperature signal corresponding to a temperature at thebearing 1024 and a proximity signal of thebalance disk 1030 relative distance to thebearing 1024. The output of thetemperature sensor 1044 may be used to control theheat exchanger 1050 and thus cool the fluid within thethrust bearing 1040. The fluid from thethrust bearing 1040 may be communicated through theheat exchanger 1050 and to theinlet pipe 1052 in a cooled state. The circulation through theheat exchanger 1050 is driven by the higher pressure caused by therotating balance disk 1030. That is, a higher pressure exists at the outer diameter of thebalance disk 1030 and thus the fluid may be communicated through the heat exchanger and back through theinlet pipe 1052. - The
speed sensor 1060 may be used to monitor the rotational speed of theshaft extension 1032 which also corresponds to the rotational speed of theshaft 20. Thespeed sensor 1060 may be located within theturbine outlet 44 or adjacent to thetemperature sensor 1044 and theproximity sensor 1046. A tooth or other indicator on the balance disk may provide the sensor with the rotational speed of the shaft. - Those skilled in the art can now appreciate from the foregoing description that the broad teachings of the disclosure can be implemented in a variety of forms. Therefore, while this disclosure includes particular examples, the true scope of the disclosure should not be so limited since other modifications will become apparent to the skilled practitioner upon a study of the drawings, the specification and the following claims.
Claims (26)
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US15/986,205 US10801512B2 (en) | 2017-05-23 | 2018-05-22 | Thrust bearing system and method for operating the same |
PCT/US2018/034163 WO2018217913A1 (en) | 2017-05-23 | 2018-05-23 | Thrust bearing system and method for operating the same |
CA3060982A CA3060982C (en) | 2017-05-23 | 2018-05-23 | Thrust bearing system and method for operating the same |
US16/573,385 US11085457B2 (en) | 2017-05-23 | 2019-09-17 | Thrust bearing system and method for operating the same |
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US201762509914P | 2017-05-23 | 2017-05-23 | |
US15/986,205 US10801512B2 (en) | 2017-05-23 | 2018-05-22 | Thrust bearing system and method for operating the same |
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US16/573,385 Continuation-In-Part US11085457B2 (en) | 2017-05-23 | 2019-09-17 | Thrust bearing system and method for operating the same |
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US11002181B2 (en) * | 2019-05-03 | 2021-05-11 | Fluid Equipment Development Company, Llc | Method and system for determining a characteristic of a rotating machine |
US20220186732A1 (en) * | 2020-12-11 | 2022-06-16 | Sapphire Motors | Integrated pump assembly with one moving part with stacked stator |
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2018
- 2018-05-22 US US15/986,205 patent/US10801512B2/en active Active
- 2018-05-23 CA CA3060982A patent/CA3060982C/en active Active
- 2018-05-23 WO PCT/US2018/034163 patent/WO2018217913A1/en active Application Filing
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US10801512B2 (en) | 2020-10-13 |
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CA3060982A1 (en) | 2018-11-29 |
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